JP5901531B2 - Axial machining equipment - Google Patents

Description

  The present invention relates to axial machining, such as drilling, boring, and milling, and more particularly to a miniature device incorporating means for applying forward and feed movement to a tool (eg, a drill bit).

  Patent application FR28881366 by applicant SETI TEC describes a drilling device that includes a drive gear for rotationally driving a bit carrier spindle and a feed gear connected to the bit carrier spindle by a screw connection.

  A similar device is shown in FIG. In this figure, reference numerals are the same as those used below to refer to the same or similar components.

  Vibration drilling devices are also known from the following publications: WO2008 / 000935A1, DE102005002462B4, US7510024B2, FR2907695, and US2007 / 209913.

  Vibration assistance helps to improve drilling quality, extend tool life, and improve the reliability of the method by eliminating the risk of chip fragmentation and clogging.

  In publications FR2907695, US7510024, and US2007 / 209813, periodic vibrations are generated by the cam without rolling members. This causes friction against the cam, which generates heat and noise. In addition, the vibration frequency is an integer multiple of the difference in rotational speed between the feed gear and the spindle or housing, and this difference is directly related to the cam periodic frequency, resulting in good fragmentation of the chips. The optimal vibration frequency is not always obtained.

  In Patent DE102005 / 002462, a spring applies a return force to a rolling bearing including a raceway that is waved in the direction of travel of the drill bit for the purpose of generating axial vibration. When the axial pressure on the drill bit is large, there is a possibility that the rolling member stops rolling on the wavy path and the bit stops periodic vibration. In order to avoid such drawbacks, the spring must have a very high stiffness and can result in a bearing that is oversized. This causes an increase in cost and size.

  Furthermore, the device is attached to the end of the spindle, and in an advance system this adds to the overall size and makes it more complex.

French Patent No. 2881366 International Publication No. 2008/000935 German Patent No. 102005002462 US Pat. No. 7510024 French Patent No. 2907695 US Patent Application Publication No. 2007/209913 German Patent Application Publication No. 102005/002462

  There is a need to further improve drilling equipment, and in particular, equipment for machining large sized aircraft workpieces such as airframes or wing parts.

Accordingly, the present invention provides an axial machining apparatus with a tool carrier spindle that is rotatable within a housing, the housing automatically advancing the spindle relative to the housing by the action of a rotationally driven tool carrier spindle. A transmission system including a feed gear coupled on the spindle with a screw .

  The apparatus preferably includes an elastic return member that biases the feed gear in a first axial direction opposite to the forward direction of the spindle (ie, the direction of movement during machining). The device rolls on an undulating track having a undulating (wavy) axial component, thereby periodically energizing the feed gear to provide a second opposite to the first direction. A first rolling bearing having a rolling member that is moved in a direction so that rotation of the spindle occurs concomitantly with the axial vibration movement.

  The device of the present invention is small because the means for providing the oscillating motion are integrated inside the housing. Friction is also greatly reduced by the rolling member.

  In addition, the present invention can generate axial vibrations at a frequency associated with the rotational speed of the rotating gear, thus maintaining a constant periodic frequency per rotation regardless of presetting. . In a variant of the invention, the first bearing is in direct contact with the feed gear, so that the axial vibration frequency is directly related to the rotational speed of the rotating gear and not to the rotational speed of the tool carrier spindle. This particular advantage is lost, but there is still another advantage.

  It is advantageous for the return member to bias the feed gear in a direction opposite to the direction of advance of the spindle. This makes it possible to apply an axial force in the forward direction of the spindle using the first rolling bearing. Thus, even when the drill bit is overloaded in the axial direction, the drill bit continues to be subjected to oscillating motion. Furthermore, neither the return member nor the first rolling bearing need be oversized. Thus, the device remains easily integrated within the housing that houses the spindle transmission and advancement system.

  Since the roller can withstand a greater force than the ball, the first rolling bearing advantageously has a roller.

  The undulating track cooperates with the rolling member like a planetary gear set that acts as a step-down gear set and reduces the periodic frequency per revolution. Thus, the first bearing serves both to reduce friction and reduce vibrational motion by the planetary gear set.

The undulating track can be configured to generate an irrational number of vibration cycles per revolution that is not an integer number of the tool carrier spindle. The number of vibration cycles per rotation of the tool carrier spindle can be, for example, between 1 and 3 (excluding end values), and in particular can be equal to about 1.5 or 2.5. it can. The undulating track may have an odd number of undulations, for example a sinusoidal undulation per revolution. For example, three undulating undulations orbital path, when the rotation of the rolling member, it is possible to generate a periodic vibration of about 1 · _^1/2 per rotation of the spindle. Being a non-integer can avoid a parallel path followed by the cutting edge during drilling, thereby improving the effectiveness of fragmenting chips.

  The undulating trajectory preferably generates non-integer and irrational vibration periods per rotation of the tool carrier spindle.

  The first rolling bearing can have a flat ring and a undulating ring, with the rolling member rotating between them, the rings being fixed or movable in the apparatus. The undulation ring defines the undulation path.

  The number of rolling members between the flat ring and the undulation ring is equal to the number of undulations in the undulation ring.

  Since one of the rings is undulating, the path and subsequent rolling elements of the ring are not two-dimensional (2D) circles, but three-dimensional (3D) sine waves. Therefore, the length of the path on the flat ring and the undulation ring is different even if the ring dimensions are the same.

上式で、Ｒ１はリング上の経路半径、θは現在点によって形成される角度、Ｎは起伏数、Ａはこれらの起伏の振幅である。 The Willis equation can be applied to the present invention. Therefore, the path of the current point on the undulation ring can be described as follows:

Where R1 is the path radius on the ring, θ is the angle formed by the current point, N is the number of undulations, and A is the amplitude of these undulations.

Differentiating this equation gives the following equation:

The absolute value or “norm” of this equation helps to obtain the differential function of the curve horizontal axis, ie the length of the path s ₁ of the relief ring.

上式で、上記の積分は、第２種不完全楕円積分である。平坦リング上では、経路ｓ₂の長さは、単に円周として記述することができる。

上式で、Ｒ２はリング半径である。 Integrating the above equation helps to calculate the curve abscissa s1.

In the above equation, the above integral is a second-type incomplete elliptic integral. On the flat ring, the length of the path s ₂ can be described simply as the circumference.

Where R2 is the ring radius.

The reduction ratios r ₁ and r ₂ of the planetary gear set for the moving ring or fixed ring respectively can be described as follows:

  This calculation requires a large number of parameters and by its nature results in an irrational periodic frequency per revolution, as described in the examples below.

By making the flat and undulating rings have equal radii, ie, R1 = R2 = 20 millimeters (mm) and their amplitude is A = 0.5 mm, the reduction ratio of the planetary gear unit is r ₁ = 0.500351, r ₂ = 0.499649, approximately equal to 1.50105 vibration cycles per spindle rotation when the undulation ring is fixed, and 1.49895 per spindle rotation when the flat ring is fixed A vibration period is obtained.

Using different values of radii, i.e. R1 = 22 mm and R2 = 20 mm, and A = 0.1 mm for the same undulation number, the reduction ratio of the planetary gear set is r ₁ = 0.523821, r ₂ = 0. Is approximately equal to 476179 and gives a vibration period of 1.57146 per rotation of the spindle in the fixed undulation ring and 1.42854 per rotation of the spindle in the fixed flat ring.

  Since the periodic vibration per rotation of the spindle is an irrational number, the risk of self-sustained vibration or chattering can be avoided.

  It is particularly advantageous to have non-integer and irrational periodic vibrations per revolution, especially when performing countersink (counterboring) and counterboring operations using this apparatus. The irrational periodic vibration per rotation makes it possible to eliminate shape defects at the end of the work, especially when there is an interruption of the stroke end for a few seconds during which no advance is made. When advancing ends at the end of a stroke of a specified number of revolutions, using non-integer and irrational periodic vibrations per revolution, the resulting surface (eg, can be a cone or a plane) is , Without being subject to any local periodic vibrations permanently at one location, and therefore acceptable even in the presence of shape defects. Each periodic vibration peak is offset slightly angularly with respect to the leading periodic vibration.

  The transmission system can include a rotating gear that serves to rotationally drive the tool carrier spindle and is disposed within the housing to allow axial movement relative to the housing. The first rolling bearing can directly contact the rotating gear.

  The rotating gear can be positioned between the feed gear and the first rolling bearing, but in a variant, the feeding gear can also be positioned between the rotating gear and the first rolling bearing.

  The apparatus can have a second rolling bearing disposed between the feed gear and the rotating gear.

  The feed gear can rotate in a third rolling bearing, in particular a needle bearing. The needle bearing can more easily cope with the axial movement of the feed gear than the ball bearing.

  The elastic return member can comprise a spring washer, through which the tool carrier spindle passes. The spring washer is supported on the radially inner ring of the fourth rolling bearing through which the tool carrier spindle passes, for example, the rolling bearing has two rows of balls, which can improve the guidance accuracy. Become.

  The present invention also provides an axial machining method using the apparatus as defined above.

  The invention can be better understood upon reading the following detailed description of non-limiting embodiments of the invention and reviewing the accompanying drawings.

1 is a longitudinal sectional view of an example of a prior art device. It is a figure similar to FIG. 1 which shows an example of the drill processing apparatus formed according to this invention. It is a figure similar to FIG. 2 which shows deformation | transformation embodiment. It is a perspective view which shows an example of a undulation track. 1 is a kinematic or perspective view of an exemplary device formed in accordance with the present invention. FIG. FIG. 3 is a kinematic diagram of various embodiments of total ground temperature of the present invention. FIG. 3 is a kinematic diagram of various embodiments of total ground temperature of the present invention.

  The machining device according to the invention shown in FIG. 2, in particular a drilling device, comprises a housing 2 that houses a part of the tool carrier spindle 3 and a system 5 that automatically drives and advances the spindle 3. The system 5 is coupled to a drive motor 112 shown in FIGS. 5 and 7, which can be, for example, a pneumatic motor. The spindle 3 drives a drill bit or cutter (not shown) so as to perform, for example, axial machining such as drilling.

  Illustratively, the system 5 is similar to that described in the patent application FR28881366, and comprises a rotating gear 10 that rotates with the spindle 3 and at the same time is axially movable. The connection between the two is a sliding connection, for example, the spindle 3 can have undulations to which the corresponding spline of the rotating gear 10 engages.

  The rotating gear 10 is rotationally driven around the axis X by a driving wheel 11 coupled to a motor.

The system 5 also has a feed gear 15 that is axially movable within the housing 2 along the axis X and includes a threaded portion 16 that is screwed onto a threaded portion of the spindle 3. The spindle moves in the axial direction by turning the feed gear 15 with respect to the shaft. Illustratively, the spindle can be advanced about 0.1 mm per approximately one revolution of the spindle. The rotational speed of the spindle can be in the range of, for example, 300 to 500 revolutions per minute (rpm).

  The feed gear 15 can rotate with respect to the rotary gear 10, and a rolling bearing 17 having a rolling member such as a ball is disposed between them in the axial direction as shown in the figure.

  The feed gear 15 can rotate within the lower induction rolling bearing 18 which rotates while allowing the feed gear 15 to have a constant upward axial stroke relative to the housing 2. Plays a guiding function.

  An elastic return member 40 such as a spring washer 40 is disposed between the feed gear 15 and the bearing 18. The spring washer 40 abuts against the inner ring of the bearing 18 in the axial direction.

  The rotating gear 10 is movable inside the housing 2 along the axis X, and is urged to move upward by the spring washer 40 via the feed gear 15 and the bearing 17.

  The rolling bearing 50 is remote from the feed gear 15 and is disposed between the housing 2 and the rotating gear 10. Accordingly, the rotating gear 10 is urged to contact the bearing 50 by the spring washer 40.

  In the illustrated embodiment, the bearing 50 is a roller inserted into the cage 54 and is supported by the upper rolling bearing 55 to guide the rotating gear 10 and the shoulder of the rotating gear 10. The rolling member 51 that rotates between the undulating lower ring 53 that rests on the part 88 and defines the undulating track is presented. An example of an undulating track 100 with axial components is shown in FIG. This figure shows the radius R1 of the ring as described above and the angle θ used in calculating the number of vibration periods per spindle rotation.

  The rotation axis of each rolling member 51 can be perpendicular to the axis X as shown.

  Illustratively, the upper bearing 51 is a ball bearing, but may be any other type of bearing.

  Due to the undulating track, the roller 51 moves in the axial direction during rotation. The maximum amplitude of this axial movement can be in the range of 0.2 mm to 0.4 mm, for example. Such axial movement is transmitted to the feed gear 15 via the rotary gear 10 and thus to the tool carrier spindle 3.

  The undulating track preferably has an odd number of undulations per revolution so as to obtain a vibration frequency that is a non-integer multiple of the rotational frequency, in particular an irrational multiple.

  The system 5 includes a drive wheel 60 for driving the feed gear 15, which is coupled to the wheel 11 by a dog clutch and automatically at the end of the downward stroke of the spindle 3 so that the spindle can be lifted. The coupling can be released from the drive wheel 11.

  The wheel 60 drives the feed gear 15 at a slightly different rotational speed than the rotational speed of the rotating gear 10 so as to produce the desired forward movement on the spindle 3 in the forward direction A in a known manner.

  At the end of the forward movement of the spindle 3, the contact portion 90 supported by the spindle 3 comes into contact with the end face of the rotary gear 10, so that the drive wheel 60 moves away from the drive wheel 11. Become.

  The drive wheel 60 pulls the piston 70 that supports the seal ring 92 downward. When the drive wheel 60 is coupled to the drive wheel 11, the seal ring isolates the chamber 72 located above the piston from the pressurized air inlet 94. When the piston 70 is moved downward, the seal ring 92 interrupts the sealed support, and the pressure present on the chamber 72 drives the piston 70 downward. The drive wheels 11 and 60 are then completely decoupled and the spindle can carry out an upward movement. The valve 96 is actuated by the spindle 3 at the end of the upward movement, thereby bringing the chamber 72 to atmospheric pressure and allowing the piston 70 to be pulled up under the action of the return spring 73. The drive wheels 11 and 60 can be coupled together repeatedly.

  The transmission system can be similar to that described in patent application FR28881366.

  The variant embodiment shown in FIG. 3 differs from the embodiment of FIG. 2 in that the lower bearing 18 is replaced with a needle bearing that more easily accommodates axial movement between track paths. The spindle 3 has two rows of balls and is guided at the lower end by a bearing 99.

  The needle bearing 100 is also used to replace the upper bearing 55 that guides the rotation of the rotating gear 10.

  The upper part of the spindle 3 is rotated and guided by a ball bearing 101. The spring washer 40 is supported on the lower ring of the bearing 99 having two rows of balls.

  FIG. 5 is a schematic diagram of an example of an apparatus constructed in accordance with the present invention.

  This figure shows the connections between the main elements of the device described above. A motor 112 to which the transmission system 5 is coupled by the drive wheel 11 can also be seen.

  6 and 7, the system 5 is incorporated in a configuration in which the feed gear and the transmission gear are interchanged. The position of the return means 40 differs between the embodiment of FIG. 6 and FIG.

  Of course, the invention is not limited to the embodiment shown. In particular, the transmission and advancement system 5 can be formed in other ways.

  The term “comprising” should be understood as synonymous with “comprising at least one”.

2 Housing 3 Tool carrier spindle 5 System 10 Rotating gear 15 Gear 40 Elastic return member, spring washer 50 Rolling bearing 51 Rolling member 60 Driving wheel 70 Piston

Claims (15)

Transmission system (2) comprising a tool carrier spindle (3) rotatable in a housing (2), wherein the housing automatically advances the spindle relative to the housing by the action of the tool carrier spindle being rotationally driven An axial machining device (1), wherein the transmission system comprises a feed gear (15) screwed onto the spindle,
An elastic return member (40) for biasing the feed gear in a first axial direction opposite to the forward direction (A) of the spindle;
Rolling on an undulating path with axial components, thereby periodically energizing the feed gear (15) to move it in a second direction opposite to the first direction, the spindle saw including a first rolling bearing having a rolling member to which the rotation of the so accompanied axially oscillating motion (51) (50), a
The first rolling bearing (50) has a flat ring (52) and a undulation ring (53), the rolling member (51) rotates between them, and the undulation ring (53) A device defining a undulating trajectory, the flat ring (52) or the undulating ring (53) being fixed in the device.   The apparatus of claim 1, wherein the first rolling bearing (50) comprises a roller (51).   The apparatus according to claim 1, wherein the undulating path presents a non-integer oscillation period per rotation of the tool carrier spindle.   The apparatus according to claim 3, wherein the undulating path generates an irrational number of vibration cycles per rotation of the spindle.   A rotating gear (5) arranged in the housing (2), wherein the transmission system (5) serves to rotate the tool carrier spindle (3) and allows axial movement relative to the housing. 10. The apparatus according to any of claims 1 to 4, comprising 10).   The apparatus according to claim 5, wherein the rotating gear (10) is located between the feed gear (15) and the first rolling bearing (50).   The device according to any of claims 5 or 6, comprising a second rolling bearing (17) arranged between the feed gear (15) and the rotating gear (10).   A device according to any of the preceding claims, wherein the feed gear (15) rotates in a third rolling bearing, in particular a needle bearing (98).   The device according to any of the preceding claims, wherein the elastic return member (40) comprises a spring washer that penetrates the tool carrier spindle (3).   10. The spring washer abuts against a radially inner ring of a fourth rolling bearing through which the tool carrier spindle (3) passes, in particular a bearing (99) with two rows of balls. Equipment.   The apparatus according to any of the preceding claims, wherein the first direction is opposite to the forward direction (A) of the spindle.   12. A device according to any preceding claim, wherein the undulating track has an odd number of undulations.   The apparatus according to claim 3 or claim 4, wherein the number of vibration cycles per rotation of the tool carrier spindle is between 1 and 3. A method for performing axial machining on a workpiece using the apparatus (1) as defined in any of claims 1 to 13 . 15. A method according to claim 14 , applied to a countersink or counterboring operation.

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